US10760635B2 - Torsion spring assembly, camshaft phaser and belt or chain tightener therewith - Google Patents

Torsion spring assembly, camshaft phaser and belt or chain tightener therewith Download PDF

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Publication number
US10760635B2
US10760635B2 US16/304,756 US201716304756A US10760635B2 US 10760635 B2 US10760635 B2 US 10760635B2 US 201716304756 A US201716304756 A US 201716304756A US 10760635 B2 US10760635 B2 US 10760635B2
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Prior art keywords
torsion spring
windings
spring
damping
damping spring
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US20190277363A1 (en
Inventor
Thomas Rausch
Georg Hannig
Christoph Angermann
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Scherdel Innotec Forschungs und Entwicklungs GmbH
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Scherdel Innotec Forschungs und Entwicklungs GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
    • F16F3/02—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction
    • F16F3/04—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction composed only of wound springs
    • F16F3/06—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of steel or of other material having low internal friction composed only of wound springs of which some are placed around others in such a way that they damp each other by mutual friction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/024—Belt drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/025—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant characterised by having a particular shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • F16F1/042—Wound springs characterised by the cross-section of the wire
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2224/00—Materials; Material properties
    • F16F2224/02—Materials; Material properties solids
    • F16F2224/0208—Alloys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2234/00—Shape
    • F16F2234/02—Shape cylindrical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2236/00—Mode of stressing of basic spring or damper elements or devices incorporating such elements
    • F16F2236/08—Torsion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2236/00—Mode of stressing of basic spring or damper elements or devices incorporating such elements
    • F16F2236/08—Torsion
    • F16F2236/085—Torsion the spring being annular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/081—Torsion springs

Definitions

  • the present invention relates to a torsion spring assembly as well as a cam phaser and a belt or chain tensioner provided with a torsion spring assembly according to the invention.
  • torsion springs which may be used in a cam phaser or in a belt or chain tensioner in order to hold two movable elements of the cam phaser or two movable elements of the belt or chain tensioner in an initial position, or return the same to the initial position.
  • These torsion springs are disadvantageous in so far as undesired vibrations occur in operation, which partially involve high resonances. This renders such torsion springs unsuitable for some fields of use, in particular for fields of use involving dynamic loads.
  • a torsion spring assembly comprises a torsion spring having a cylindrical spring body of wound spring wire and with a plurality of torsion spring windings, and having first and second torsion spring ends for taking up forces in a direction of rotation, as well as a damping spring abutting the torsion spring on the inner side and having a cylindrical spring body of wound spring wire and with a plurality of damping spring windings, and having first and second damping spring wire ends.
  • the damping spring windings have their outer sides extending partially into the space formed between two respectively adjacent torsion spring windings and thus abutting in particular rounded, round or beveled inner abutment areas of respectively adjacent torsion spring windings with substantially radially outwardly directed bias.
  • a torsion spring assembly according to the invention is designed such that the damping spring windings are coupled with the torsion spring windings having the damping spring windings respectively abutting thereon.
  • this coupling is not completely rigid, but rather takes place via frictional abutment of the damping spring windings on the torsion spring windings.
  • the damping spring supports the torsion spring.
  • friction is caused between the damping spring windings and the respective abutting torsion spring windings upon rotation of the torsion spring wire ends relative to each other.
  • the torsion spring assembly according to the invention in comparison with conventional torsion springs, achieves improved spring properties, in particular an improved damping effect, a significant reduction of resonances or resonance peaks, enhanced dimensional stability and operational stability as well as a longer service life and durability.
  • the partial extension of the damping wire windings into the space formed between two respectively adjacent torsion spring windings may also be referred to as nestling of the damping spring between adjacent torsion spring windings.
  • the damping spring urges the torsion spring radially outwardly.
  • a torsion spring assembly according to the invention allows the outer dimensions of the constructional space to be retained, so that a torsion spring assembly according to the invention may be used in the same applications as well as in the same constructional space available as a conventional torsion spring.
  • a torsion spring assembly according to the invention involves merely a minor alteration of the spring characteristics.
  • the hysteresis, caused by friction and the spring rate, increases merely slightly in comparison with a conventional torsion spring as well.
  • the in particular rounded, round or beveled abutment areas of respectively adjacent torsion spring windings are provided with a sufficiently large edge radius in order to allow sufficient guiding for the damping spring, also in case of larger deformation of the torsion spring.
  • the inventors have ascertained that, by way of a larger bias of the damping spring in outward direction, the damping effect of the torsion spring assembly in its entirety can be increased.
  • the damping spring windings may have a smaller wire diameter than the torsion spring windings. In practical use, the damping spring is subject to lower loads than the torsion spring.
  • the torsion spring assembly according to the invention is suitable for arbitrary dynamic applications, and thus for all applications in which force take-up and/or a cushioning effect in the direction of rotation is to be achieved and in which a dynamic load is present.
  • a torsion spring assembly according to the invention is particularly advantageous for use in a cam phaser for a motor vehicle engine, or for a belt or chain tensioner for maintaining the tension of a V-belt or ribbed V-belt or a chain in a work unit, such as an internal combustion engine.
  • the torsion spring assembly according to the invention can be retrofitted rapidly and without any problem in already existing cam phasers or belt or chain tensioners, as the dimension of the torsion spring assembly may correspond to the dimension of a conventional torsion spring.
  • the spring wire ends of the torsion spring allow for advantageous connection of the torsion spring assembly, in particular in the cam phaser or in the belt or chain tensioner.
  • the spring wire ends of the torsion spring can efficiently take up setting forces, in particular in adjusting the cam phaser or in rotating the belt or chain tensioner.
  • the torsion spring and the damping spring can be manufactured separately and be united to the torsion spring assembly according to the invention at a later time, either manually or with the aid of a machine. This permits rapid and efficient production.
  • the respectively adjacent torsion spring windings are coupled with each other via the damping spring winding located therebetween. This results in enhanced spring properties of the torsion spring assembly.
  • the outer diameter of the damping spring is greater than the inner diameter of the torsion spring, in particular greater by a value in the range between 5 and 50% of the wire diameter of the damping spring, so that in the abutting state of torsion spring and damping spring, respectively adjacent torsion spring windings are coupled with each other via the damping spring winding located therebetween.
  • the torsion spring windings each have a substantially rectangular cross-sectional area with rounded or beveled transitions between the radial inner side thereof and the axial lower side thereof, and between the radial inner side thereof and the axial upper side thereof, with these rounded or beveled transitions constituting the abutment areas of the damping spring windings.
  • This permits particularly advantageous coupling of the damping spring windings with the torsion spring windings.
  • This provides for a sufficiently large abutment area between torsion spring windings and damping spring windings, which ensures good guidance of the damping spring windings also in case of deformation of the torsion spring assembly.
  • the width of the radial upper side and lower side of the cross-sectional area of the spring windings of the torsion spring is greater than the height of the axial inner side and outer side.
  • the torsion spring windings each have a round, oval, elliptic or multi-arc cross-sectional area with round or rounded transitions between the radial inner side thereof and the axial lower side thereof and between the radial inner side thereof and the axial upper side thereof, with these round or rounded transitions constituting the abutment areas of the torsion spring windings.
  • This permits particularly advantageous coupling of the damping spring windings with the torsion spring windings.
  • the damping spring windings have a round, oval, elliptic or multi-arc cross-sectional area. This permits particularly advantageous coupling between the torsion spring windings and the damping spring windings. There is provided a sufficiently large abutment area between torsion spring windings and damping spring windings, thus ensuring good guidance of the damping spring windings also in case of deformation of the torsion spring assembly.
  • the damping spring windings have their outer sides extending into the space formed between two respectively adjacent torsion spring windings across a major part of the inside of the cylindrical spring body of the torsion spring and abutting rounded abutment areas of respectively adjacent torsion spring windings with substantially radially outwardly directed bias.
  • the damping spring may have approx. one half to three windings less than the torsion spring.
  • cylindrical spring body of the torsion spring and the cylindrical spring body of the damping spring each have the same spring axis, and the cylindrical spring body of the damping spring and the cylindrical spring body of the portion spring are arranged concentrically within each other.
  • the spring wire ends of the torsion spring are each bent in substantially radially outward direction. This allows for particularly easy connection to the respective connecting sites, such as e.g. to a stator and a rotor of the cam phaser or to an anchor plate and a pivot arm of the belt or chain tensioner.
  • the damping spring has two spring wire ends that are each bent inwardly.
  • a biasing tool can be applied to these ends in particularly easy manner in order to bias the damping spring and introduce the same into the torsion spring.
  • the spring windings of the torsion spring and the damping spring have an identical pitch angle, in particular a pitch angle of 1° to 3°.
  • the spring wire ends of the torsion spring and/or the damping spring are formed without pitch or gradient. This allows for particularly easy connection of the torsion spring assembly.
  • the torsion spring and/or the damping spring are made of spring steel.
  • the invention also relates to a torsion spring assembly comprising: a torsion spring having a cylindrical spring body of wound spring wire and with a plurality of torsion spring windings, and having first and second torsion spring ends for taking up forces in a direction of rotation, as well as a damping spring abutting the torsion spring on the outer side and having a cylindrical spring body of wound spring wire and with a plurality of damping spring windings, and having first and second damping spring wire ends.
  • the damping spring windings have their inner sides extending partially into the space formed between two respectively adjacent torsion spring windings, and abutting in particular rounded, round or beveled outer abutment areas of respectively adjacent torsion spring windings with substantially radially inwardly directed bias.
  • the invention also relates to a cam phaser for a motor vehicle engine.
  • the cam phaser comprises a stator for rigid connection to a cylinder head, which has a substantially cylindrical stator base body including a front wall, a rear wall and a circumferential wall having an inwardly directed inner peripheral surface, as well as two stator webs extending radially inwardly from the inner peripheral surface, a rotor for rigid connection to a camshaft, which is rotatably arranged in the stator and which has a substantially cylindrical base body having an outer peripheral surface and at least two outwardly directed rotor wings, with pressure spaces adapted to be filled or filled with a hydraulic medium being formed between the inner surfaces of the front wall and the rear wall, between the stator webs of the stator and the rotor wings of the rotor as well as between the inner peripheral surface of the stator and the outer peripheral surface of the rotor, as well as a spring receiving space in which a torsion spring assembly of the kind described herein is arranged in such
  • the cam phaser according to the invention is used for varying the control times or valve opening times of inlet and exhaust valves of a motor vehicle engine during operation, thus achieving more efficient fuel consumption while obtaining at the same time higher performance and higher torques.
  • the cam phaser may be coupled to the crankshaft of the motor vehicle engine via a belt, a timing chain or spur gears.
  • a belt according to the invention is understood to comprise the elements toothed belt, timing belt, V-belt or combinations of these elements as well.
  • the torsion spring assembly permits enhanced damping as well as a significant reduction of resonances or resonance peaks between stator and rotor. This leads to longer durability as well as better controllability and adjustability of the cam phaser.
  • the invention also relates to a belt or chain tensioner for maintaining the tension of a V-belt, a ribbed V-belt or a chain in a work unit, such as an internal combustion engine.
  • the belt or chain tensioner comprises an anchor plate for connection to the work unit, a pivot arm which is rotatably supported with respect to the anchor plate and which has a belt or chain pulley for guiding the V-belt, the ribbed V-belt or the chain, with said belt or chain pulley being rotatably supported in particular at the end portion of the pivot arm remote from the pivot axis of the pivot arm, as well as a spring receiving space in which a torsion spring assembly of the type described herein is arranged such that the first torsion spring wire end is non-rotatably connected to the anchor plate and the second torsion spring wire end is non-rotatably connected to the pivot arm.
  • the belt or chain tensioner according to the invention is used for reliably maintaining the tension of the belt or chain.
  • a belt is understood to comprise also the elements toothed belt, timing belt, V-belt or combinations of these elements.
  • the rotatable connection of the pivot arm to the anchor plate via the torsion spring assembly permits easy application and correct, automatic tensioning of the belt or chain as well as safe operation of the belt or chain tensioner.
  • the pivot arm may be supported via a ball bearing, a roller bearing, a plain bearing or the like. This ensures easy pivoting of the pivot arm with respect to the anchor plate.
  • FIG. 1 shows a perspective view, as seen obliquely from above, of a torsion spring assembly comprising a torsion spring and an internal damping spring according to an embodiment of the present invention
  • FIG. 2 shows a plan view of the torsion spring assembly of FIG. 1 ;
  • FIG. 3 shows a cross-sectional view along a cross-sectional plane A-A of the torsion spring assembly of FIGS. 1 and 2 , said plane extending through the spring axis;
  • FIG. 4 shows an enlarged detailed view of three torsion spring windings and two damping spring windings of the cross-sectional view of FIG. 3 ;
  • FIG. 5 shows a perspective view of a cam phaser, clearly showing a stator and the torsion spring assembly of FIGS. 1 to 4 arranged in the stator;
  • FIG. 6 shows a perspective view of the cam phaser of FIG. 5 , which clearly shows a rotor
  • FIG. 7 shows a perspective view of a belt or chain tensioner comprising an anchor plate, a pivot arm rotatably supported thereon and having a belt or chain pulley, along with the torsion spring assembly of FIGS. 1 to 4 connecting the anchor plate to the pivot arm; and
  • FIG. 8 shows a cross-sectional view along a cross-sectional plane B-B extending through the longitudinal axis of the pivot arm of FIG. 7 .
  • FIG. 1 shows a perspective view, as seen obliquely from above, of a torsion spring assembly 2 comprising a torsion spring 4 and an internal damping spring 20 .
  • the torsion spring 4 of wound spring wire comprises torsion spring windings 6 forming a cylindrical spring body extending about a central axis or spring axis.
  • the torsion spring 4 in exemplary manner comprises four torsion spring windings 6 as well as a first torsion spring wire end 8 and a second torsion spring wire end 10 .
  • the torsion spring 4 may also have a larger or lesser number of torsion spring windings 6 .
  • the torsion spring 4 is designed to receive forces acting thereon via its torsion spring wire ends 8 and 10 in the direction of rotation.
  • the torsion spring windings 6 have a radial inner side 12 with an inner diameter and a radial outer side 14 with an outer diameter, with the inner diameter and the outer diameter being different from each other and being adapted to be matched to the particular application.
  • the torsion spring wire ends 8 , 10 extend radially outwardly, preferably at approx. right angles, from the spring body of the torsion spring 4 .
  • the damping spring 20 made of a wound spring wire as well, comprises damping spring windings 22 which also form a cylindrical spring body extending about the same central axis or spring axis as the torsion spring 4 .
  • the damping spring 20 illustrated here comprises three damping spring windings 22 in exemplary manner. It is of course also possible for the damping spring 22 to have a larger or lesser number of windings 22 , with the damping spring 20 in particular having 1 to 3 windings less than the torsion spring 4 .
  • the damping spring 20 comprises first and second damping spring wire ends 24 and 26 extending radially a certain distance into the interior of the cylindrical spring body. Optionally, the spring ends may also be directed radially outwardly and thus be used on one side as anti-rotation device.
  • the cylindrical spring body of the torsion spring 4 and the cylindrical spring body of the damping spring 20 are arranged concentrically within each other.
  • the damping spring 20 abuts the torsion spring 4 on the inner side.
  • the damping spring windings 22 have their outer sides extending partially into the space 28 formed between two adjacent torsion spring windings 6 each.
  • the damping spring windings 22 abut inner abutment areas of respectively adjacent torsion spring windings 6 with radially outwardly directed bias.
  • the abutment areas on the side of the torsion spring windings are constituted by the rounded or beveled transitions from the radial inner side 12 to the axial lower side 18 and the axial upper side 16 of the respective torsion spring windings 6 . These abutment areas on the side of the torsion spring windings may be rounded, round or beveled.
  • the damping spring abuts the torsion spring externally, and the damping spring windings have their inner sides extending partially into the external space formed between two adjacent torsion spring windings each.
  • the damping spring 20 In a non-abutting state of torsion spring 4 and damping spring 20 , the damping spring 20 has a larger outer diameter than the inner diameter of the torsion spring 4 .
  • the outer diameter of the damping spring 20 may be larger by a value which is in the range between 5% and 50% of the diameter of the damping spring windings 22 . In the abutting state, this permits the damping spring windings 22 to abut inner abutment areas of respectively adjacent torsion spring windings 6 with radially outwardly directed bias, and allows that respectively adjacent torsion spring windings 6 are coupled with each other via the damping spring winding 22 located therebetween.
  • the torsion spring windings 6 are arranged in parallel or in axially aligned manner with respect to each other, with adjacent spring windings being arranged at an axial spacing from each other, which corresponds to a height of 1% to 50% of the height of one torsion spring winding 6 .
  • the damping spring windings 22 extend across a major part of the height of the inside of the cylindrical spring body of the torsion spring 4 to respective end abutment sections which, as seen in the direction of rotation, are each located in front of the torsion spring wire ends 8 and 10 and from which the first and second damping spring wire ends 24 and 26 are bent inwardly.
  • the torsion spring windings 6 and the damping spring windings 22 have an identical pitch angle, which is in a range from 1° and 10°, in particular in a range from 1° to 3°.
  • FIG. 2 shows a plan view of the torsion spring assembly 2 along the central axis or spring axis. The view clearly shows the torsion spring 4 along with the internally abutting damping spring 22 .
  • the damping spring wire ends 24 , 26 in exemplary manner extend at an angle from 5° to 75°, in particular at an angle from 10° to 45°, radially into the inner space formed by the cylindrical spring body.
  • the damping spring wire ends extend radially outwardly in the aforementioned angle range.
  • the torsion spring wire ends 8 , 10 are each bent radially outwardly from an end of a lower and upper torsion spring winding 6 , respectively.
  • the torsion spring wire ends 8 , 10 may be bent radially outwardly at an angle between 80° and 100°, in particular at an angle of 90°, starting from the end of the respective torsion spring winding 6 where these ends begin.
  • the torsion spring wire ends 8 , 10 in the embodiment illustrated, are arranged at an angle of approx. 130° to 160°, in particular of 140° to 150°, with respect to each other as measured in the direction of rotation.
  • the torsion spring wire ends 8 , 10 may also be arranged at a different angle with respect to each other.
  • FIG. 3 illustrates a cross-sectional view along a cross-sectional plane A-A of the torsion spring assembly 2 , which extends through the spring axis.
  • the torsion spring windings 6 each having a substantially rectangular cross-sectional area and the damping spring windings 22 having a round cross-sectional area, are clearly visible.
  • the damping spring windings 22 abut the rounded inner abutment areas on the side of the torsion spring windings with outwardly directed bias, said abutment areas bearing numeral 30 herein.
  • the abutment areas 30 on the side of the torsion spring windings which are constituted by the rounded or beveled transitions from the radial inner side 12 to the axial lower side 18 and to the axial upper side 16 of the respective torsion spring windings 6 , are clearly visible in FIG. 3 .
  • the torsion spring wire end 10 beginning at the upper torsion spring winding 6 is clearly visible in FIG. 2 .
  • the torsion spring wire ends 8 , 10 may be formed without pitch or gradient. This holds also for the damping spring wire ends 24 , 26 .
  • FIG. 3 clearly shows that the width of the axial upper side 16 and the axial lower side 18 of the torsion spring windings 22 is greater than the height of the radial inner side 12 and the radial outer side 14 of the torsion spring windings 22 . This achieves a particularly compact construction of the torsion spring assembly 2 .
  • the torsion spring windings 4 may have a round, oval, elliptic or multi-arc cross-sectional area in other embodiments not illustrated here.
  • the damping spring windings 22 may have a round, oval, elliptic or multi-arc cross-sectional area in other embodiments not illustrated here.
  • FIG. 4 shows an enlarged detailed view of three torsion spring windings 6 and two damping spring windings 22 of the cross-sectional view of FIG. 3 .
  • the space 28 between two adjacent torsion spring winding 6 each is clearly visible.
  • Also clearly visible are the rounded or beveled inner abutment areas 30 on the side of the torsion spring windings, on which the damping spring windings 22 abut with bias.
  • FIG. 5 shows a perspective view of a cam phaser 32 , permitting a clear view of a stator 34 and the torsion spring assembly 2 arranged within the stator 34 .
  • FIG. 6 shows a perspective view of the cam phaser 32 , permitting a clear view of a rotor 48 arranged within the stator 34 .
  • the cam phaser 32 comprises a stator 34 and a rotor 48 rotatably arranged in the stator 32 .
  • a toothed driving member connecting portion 40 for connecting the cam phaser 32 to a drive unit.
  • the stator 34 may be connected to a cylinder head, not illustrated.
  • the stator 34 comprises a substantially cylindrical stator base body 36 and a front wall, not illustrated and forming an upper wall in FIG. 6 , a rear wall, not illustrated and forming a lower wall in FIG. 6 , which is conceivable as closing the rotor 48 from below, as well as a circumferential wall 38 .
  • the circumferential wall 38 comprises an inwardly directed inner peripheral surface 39 from which at least one, in the exemplary embodiment three, stator webs 46 extend radially inwardly.
  • the portion located in circumferential direction between the stator webs 48 defines a rotor wing receiving space 44 .
  • the stator 34 comprises three stator webs 46 in exemplary manner.
  • the stator webs 46 extend as far as a rotor outer peripheral surface 50 of rotor 48 .
  • the rotor 48 comprises a substantially cylindrical base body having the rotor outer peripheral surface 50 . From this rotor outer peripheral surface 50 , there extends at least one rotor wing 52 , in the embodiment three rotor wings 52 in exemplary manner, in radially outward direction. The rotor wings 52 extend as far as the inner peripheral surface 39 of the stator 34 .
  • the rotor 48 has a camshaft mounting opening 54 arranged centrally therein, in which a camshaft for a motor vehicle engine can be fixedly mounted.
  • the stator 34 and the rotor 48 define a cylindrical spring receiving space 35 , having the torsion spring assembly 2 arranged therein.
  • the cylindrical spring receiving space 35 is clearly visible in FIG. 5 . It extends from the upper face of the stator 34 downwardly towards the rotor 48 and has a height corresponding approx. to the block dimensions of the torsion spring assembly 2 , and an inner diameter corresponding approx. to the outer diameter of the torsion spring windings 6 of the torsion spring assembly 2 .
  • the torsion spring assembly 2 is arranged in the spring receiving space 35 of the cam phaser 32 such that the torsion spring windings 6 abut the peripheral surface of the spring receiving space 35 , or are arranged at a slight radial spacing from the same, such that the first torsion spring wire end 8 is non-rotatably connected to stator 34 and the second torsion spring wire end 10 is non-rotatably connected to rotor 48 .
  • the torsion spring wire end 8 abuts a supporting pin 42 of stator 34 , which takes up a resetting force of the torsion spring assembly 2 .
  • the supporting pin 42 may axially project from the face of stator 34 in upward direction.
  • the opposite torsion spring wire end which is not visible in FIGS. 5 and 6 , is connected to rotor 48 .
  • a torsion spring assembly 2 arranged in this manner permits exact control or regulation of the adjustment angle of the camshaft. Moreover, use of the torsion spring assembly 2 can ensure more sufficient fuel consumption of the motor vehicle engine. Due to the mechanical adjustability of the torsion spring assembly 2 , particularly simple resetting of the rotor 48 in the cam phaser 32 is rendered possible.
  • FIG. 7 shows a perspective view of a belt or chain tensioner 58 for maintaining the tension of a V-belt, a ribbed V-belt or a chain in a work unit.
  • FIG. 8 shows a cross-sectional view of the belt or chain tensioner 58 along a cross-sectional plane B-B, intersecting the pivot arm 68 in the direction of the longitudinal axis thereof.
  • the belt or chain tensioner 58 comprises an anchor plate 60 for a preferably fixed connection to the work unit.
  • the anchor plate 60 has mounting portions 62 provided therein which are formed as recesses, which in the example illustrated are present in a number of three. Of course, there may also be a larger or lesser number of mounting portions provided in the anchor plate.
  • the belt or chain tensioner 58 has a pivot arm 68 rotatably supported with respect to the anchor plate 60 , said pivot arm 68 comprising a belt or chain pulley 72 for guiding the belt or chain, which is rotatably supported in particular at the end portion of the pivot arm 68 remote from the pivot axis of pivot arm 68 .
  • the pivot arm 68 is arranged preferably on an upper side 64 of anchor plate 60 . It is of course also possible that the spring receiving space 66 is formed by the anchor plate 60 only or by the pivot arm 68 only.
  • the torsion spring assembly 2 permits simple and reliable biasing of the pivot arm 68 . This has the effect that the rotatably supported belt or chain pulley 72 is permanently in contact with the V-belt, the ribbed V-belt or the chain and keeps the same under tension. Slippage of the V-belt, the ribbed V-belt or the chain is thus avoided in particularly reliable manner.
  • the anchor plate 60 and the pivot arm 68 define a cylindrical spring receiving space 66 having the torsion spring assembly 2 arranged therein.
  • FIG. 8 clearly shows that a cylindrical recess in the anchor plate 60 as well as an aligned cylindrical recess in the pivot arm 68 together form the cylindrical spring receiving space 66 having the torsion spring assembly 2 arranged therein.
  • the cylindrical spring receiving space 66 has a height corresponding approx. to the block dimensions of the torsion spring assembly 2 , and an inner diameter corresponding approx. to the outer diameter of the torsion spring windings 6 of the torsion spring assembly 2 .
  • the torsion spring assembly 2 is arranged in the spring receiving space 66 such that the torsion spring windings 6 abut the peripheral surface of the spring receiving space 66 or are arranged at a slight radial spacing from the same, that the first torsion spring wire end 8 is non-rotatably connected to the anchor plate 60 and that the second torsion spring wire end 10 is non-rotatably connected to the pivot arm 68 via a supporting pin 70 .
  • the torsion spring wire end 8 abuts the supporting pin 42 of pivot arm 68 , which takes up a resetting force of the torsion spring assembly 2 .
  • the supporting pin 68 may project beside the spring receiving space 74 from the face of the pivot arm 68 in axially upward direction.
  • the opposite torsion spring wire end is connected to anchor plate 60 .
  • the belt or chain pulley 72 is rotatably supported using suitable fastening means, with the belt or chain pulley 72 being arranged on the side of the pivot arm 68 facing away from the anchor plate 60 .
  • suitable fastening means With a corresponding design of the belt or chain pulley 72 , it is of course also possible to arrange the belt or chain pulley 72 on the side facing towards the anchor plate 60 . This permits a particularly compact form of construction for a belt or chain tensioner.
  • the belt or chain pulley 72 in the present embodiment has five notches 76 extending circumferentially around the belt or chain pulley 72 in order to ensure exact guiding of the V-belt, the ribbed V-belt or the chain. It is of course also possible to arrange a larger or lesser number of notches 76 in the belt or chain pulley 72 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Springs (AREA)
US16/304,756 2016-05-27 2017-05-26 Torsion spring assembly, camshaft phaser and belt or chain tightener therewith Active US10760635B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102016109783.7A DE102016109783A1 (de) 2016-05-27 2016-05-27 Drehfederanordnung sowie Nockenwellenversteller und Riemen- oder Kettenspanner damit
DE102016109783.7 2016-05-27
DE102016109783 2016-05-27
PCT/EP2017/062788 WO2017203041A1 (de) 2016-05-27 2017-05-26 Drehfederanordnung sowie nockenwellenversteller und riemen- oder kettenspanner damit

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EP (1) EP3464930B1 (zh)
CN (1) CN109416099B (zh)
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220364621A1 (en) * 2021-05-13 2022-11-17 Moffitt, LLC Methods and apparatus for a 3d-printed spring

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110131344A (zh) * 2019-05-20 2019-08-16 诸暨市旋和弹簧技术有限公司 一种三螺旋弹簧及制作方法
CN114165530B (zh) * 2022-02-08 2022-05-10 深圳市悦成汽车技术有限公司 一种电动车用自动变速器输入轴减振结构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5464197A (en) 1994-08-15 1995-11-07 Ecclesfield; George Torsion spring having an adjustable spring rate
US6220586B1 (en) * 1999-09-21 2001-04-24 Precision Products Group Multiple torsion spring and methods of use
US20130233113A1 (en) 2010-11-22 2013-09-12 Yamaha Hatsudoki Kabushiki Kaisha Combination torsion spring, and shift mechanism provided with same
US10309270B2 (en) * 2014-04-01 2019-06-04 Schaeffler Technologies AG & Co. KG Camshaft adjuster

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1405732A1 (de) * 1960-08-22 1969-05-29 Richard Appenrodt Herstellung eines Kombi-Krankenfahrstuhles fuer Zimmer,Strasse,Treppe und Gelaende nach dem Prinzip des Treppenbefahrers fuer Gehbehinderte
JPS6122945U (ja) * 1984-07-16 1986-02-10 株式会社 オハラ 回転装置
US7217207B1 (en) * 2005-11-03 2007-05-15 The Gates Corporation Tensioner
CN101201088A (zh) * 2006-12-15 2008-06-18 上海通运汽车科技有限公司 一种变刚度螺旋扭力弹簧
CA2740322C (en) * 2008-10-27 2018-09-04 Litens Automotive Partnership Over-running decoupler with torque limiter
US20110015017A1 (en) * 2009-07-17 2011-01-20 Alexander Serkh Tensioner
DE102010010733A1 (de) * 2010-03-09 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Schaltbarer Schlepphebel

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5464197A (en) 1994-08-15 1995-11-07 Ecclesfield; George Torsion spring having an adjustable spring rate
US6220586B1 (en) * 1999-09-21 2001-04-24 Precision Products Group Multiple torsion spring and methods of use
US20130233113A1 (en) 2010-11-22 2013-09-12 Yamaha Hatsudoki Kabushiki Kaisha Combination torsion spring, and shift mechanism provided with same
US10309270B2 (en) * 2014-04-01 2019-06-04 Schaeffler Technologies AG & Co. KG Camshaft adjuster

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220364621A1 (en) * 2021-05-13 2022-11-17 Moffitt, LLC Methods and apparatus for a 3d-printed spring

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EP3464930B1 (de) 2020-07-29
WO2017203041A1 (de) 2017-11-30
DE102016109783A1 (de) 2017-11-30
CN109416099B (zh) 2020-09-11
US20190277363A1 (en) 2019-09-12
EP3464930A1 (de) 2019-04-10
CN109416099A (zh) 2019-03-01

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